WO2015008325A1 - Dispositif d'engrenage d'entraînement - Google Patents

Dispositif d'engrenage d'entraînement Download PDF

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Publication number
WO2015008325A1
WO2015008325A1 PCT/JP2013/069259 JP2013069259W WO2015008325A1 WO 2015008325 A1 WO2015008325 A1 WO 2015008325A1 JP 2013069259 W JP2013069259 W JP 2013069259W WO 2015008325 A1 WO2015008325 A1 WO 2015008325A1
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WO
WIPO (PCT)
Prior art keywords
gear
planetary gear
external
planetary
mechanisms
Prior art date
Application number
PCT/JP2013/069259
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English (en)
Japanese (ja)
Inventor
久保　愛三
伸▲よし▼ 杉谷
Original Assignee
株式会社アルケミカ
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社アルケミカ filed Critical 株式会社アルケミカ
Priority to PCT/JP2013/069259 priority Critical patent/WO2015008325A1/fr
Priority to PCT/JP2014/068161 priority patent/WO2015008661A1/fr
Priority to EP14826409.6A priority patent/EP3023672A4/fr
Priority to JP2015527263A priority patent/JP6122119B2/ja
Priority to US14/905,567 priority patent/US10203028B2/en
Priority to CN201480040592.8A priority patent/CN105556174B/zh
Publication of WO2015008325A1 publication Critical patent/WO2015008325A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
    • F16H2048/364—Differential gearings characterised by intentionally generating speed difference between outputs using electric or hydraulic motors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/72—Electric energy management in electromobility

Definitions

  • the present invention relates to a drive gear device, and more particularly, to a drive gear device capable of transmitting rotational motion or power (torque) in two paths.
  • Patent Document 1 discloses a differential gear device 110 shown in the configuration diagram of FIG.
  • the differential gear mechanism 110 includes two sets of planetary gear mechanisms 120 a and 120 b, and the externally toothed sun gear members 123 a and 123 b of the planetary gear mechanisms 120 a and 120 b are coupled to each other via an inner coupling member 122.
  • Outer coupling members 127a and 127b are coupled to the inner gear members 126a and 126b of the respective planetary gear mechanisms 120a and 120b, and gear portions 128a and 128b meshing with the gear member 129 are formed on the axially perpendicular end surfaces of the outer coupling members 127a and 127b.
  • a driving force is input to the inner coupling member 122, the driving force is output from the planet carriers 125a and 125b.
  • the distribution of the driving force and the rotation speed can be controlled.
  • Patent Document 2 discloses a spur gear differential shown in the perspective view of FIG.
  • the spur gear differential device includes first and second sun gears 203 and 205 and first and second planetary gears 207 and 209 that mesh with each other.
  • the first planetary gear 207 meshes only with the first sun gear 203
  • the second planetary gear 209 meshes only with the second sun gear 205.
  • the first and second sun gears 203 and 205 have the same number of teeth and different tip diameters.
  • One of the first and second sun gears 203 and 205 has a positive dislocation and the other has a negative dislocation.
  • Patent Document 3 discloses a transmission device shown in the block diagram of FIG.
  • the transmission device includes planetary gear sets 318 and 319 coupled to the output shafts 316 and 317 and a shift mechanism 322 between the output shafts 316 and 317, respectively.
  • the shift mechanism 322 can be switched to the shift positions S1 and S2.
  • the shift position S1 can handle braking and driving by rotating in the same direction, and the left and right axes can be rotated in reverse at the shift position S2.
  • JP 2006-214530 A US Patent Application Publication No. 2011/0245012 US Patent Application Publication No. 2010/0323838
  • the gear member 129 is arranged non-parallel to the central axes of the planetary gear mechanisms 120a and 120b, the structure becomes complicated and the manufacturing cost increases, and the gear member 129 and Friction loss occurs due to meshing of the outer coupling members 127a and 127b with the gear portions 128a and 128b. Further, since the gear member 129 is disposed in the radial direction with respect to the central axis of the planetary gear mechanisms 120a and 120b, and the torsion torque acts on the outer coupling members 127a and 127b, it is difficult to reduce the size and weight.
  • the spur gear differential shown in FIG. 10 is a stepped planetary gear mechanism that functions as a simple differential gear mechanism that allows a difference in rotation between the left and right wheels of the vehicle.
  • it is necessary to rotate the carrier that rotatably supports the first planetary gear 207 and the second planetary gear 209. In that case, the configuration for rotating the carrier is complicated and large.
  • the transmission device of FIG. 11 has a first and second planetary gear sets 318 and 319 that are different in configuration and are asymmetrical in configuration.
  • the present invention is intended to provide a drive gear device that can be easily reduced in size and weight with a simple configuration.
  • the present invention provides a drive gear device configured as follows.
  • the drive gear device includes: (a) an externally toothed sun gear member on which an externally toothed sun gear is formed; a planetary gear member on which a planetary gear that meshes with the externally toothed sun gear; and an internal tooth that meshes with the planetary gear. And a planet carrier that supports the planetary gear member so that it can revolve and rotate around the external gear sun gear.
  • a second planetary gear mechanism ; (b) a coupling member that coaxially couples the externally toothed sun gear members of the first and second planetary gear mechanisms; and (c) the inner part of the first planetary gear mechanism.
  • the planetary gear mechanism is arranged so as to be parallel and rotatable with the rotation center axis of the external sun gear.
  • a first auxiliary gear member formed; (d) a second gear meshing with the external teeth of the internal gear member of the second planetary gear mechanism; and the first gear disposed coaxially with the second gear.
  • a second auxiliary gear member disposed in parallel with the shaft and rotatably.
  • the external teeth of the internal gear member of the first and second planetary gear mechanisms mesh with the first and second gears of the first and second auxiliary gear members, and the first and second auxiliary gears are engaged. Since the third and fourth gears of the gear member mesh with each other, the rotational torque input to the coupling member is evenly distributed to the planet carriers of the first and second planetary gear mechanisms.
  • the first and second auxiliary gear members are arranged in parallel with the rotation center axis of the external sun gear member of the first and second planetary gear mechanisms, and the first and second auxiliary gears are arranged. No driving force is transmitted to the first and second gears of the member, and the friction loss is small. Further, the first and second auxiliary gear members do not need to revolve around the internal gear members of the first and second planetary gear mechanisms. Therefore, the drive gear device has a simple configuration and can be easily downsized.
  • the first and second planetary gear mechanisms are arranged so as to be parallel to and rotatable with respect to the rotation center axis of the external gear sun gear, and with the external teeth of the internal gear member of the first planetary gear mechanism.
  • a third auxiliary gear member is arranged so as to be parallel to and rotatable with respect to the rotation center axis of the external gear sun gear, and with the external teeth of the internal gear member of the first planetary gear mechanism.
  • the third auxiliary gear member can control the difference in rotational torque and rotational speed distributed to the planet carriers of the first and second planetary gear mechanisms. Since the rotation for transmitting the rotational torque and the rotation of the third auxiliary gear member for controlling the distribution of the rotational torque and the difference in the rotational speed are completely separated, the controllability is very good. Furthermore, even when the mechanism for driving the third auxiliary gear fails, the mechanical operation for distributing the rotational torque is maintained safely.
  • the external tooth sun of the first and second planetary gear mechanisms is fixed to the coupling member and coaxial with the rotation center axis of the external tooth sun gear of the first and second planetary gear mechanisms.
  • An intermediate gear member disposed between the gears and formed with external teeth is further provided.
  • the output can be distributed to the planet carriers of the first and second planetary gear mechanisms by disposing the drive source outside the drive gear device and transmitting the drive force to the intermediate gear member.
  • the diameter of the tip circle of the external tooth of the intermediate gear member is smaller than the diameter of the tip circle of the external tooth of the internal gear member of the first and second planetary gear mechanisms.
  • the drive gear device can be downsized, or the drive source and the drive gear device can be brought close to each other to be compact.
  • an electric motor having a rotating shaft protruding at both ends is disposed between the first planetary gear mechanism and the second planetary gear mechanism.
  • the externally toothed sun gear member of the first planetary gear mechanism is coupled to one end side of the rotating shaft of the electric motor.
  • the external gear sun gear member of the second planetary gear mechanism is coupled to the other end side of the rotating shaft of the electric motor.
  • the rotation shaft of the electric motor is arranged coaxially with the rotation center shaft of the external gear sun gear of the first and second planetary gear mechanisms.
  • the coupling member is constituted by the rotating shaft of the electric motor.
  • an electric motor can be incorporated in the drive gear device, and the drive system can be configured integrally by combining the electric motor, the speed reducer, and the differential, thereby reducing the size.
  • the drive gear device of the present invention can be easily reduced in size and weight with a simple configuration.
  • Example 1 It is a block diagram of a drive gear apparatus.
  • Example 1 It is a perspective view which shows meshing
  • Example 1 It is a perspective view which shows meshing
  • Example 1 It is a perspective view which shows meshing
  • Example 1 It is a perspective view which shows meshing
  • Example 1 It is a top view of meshing
  • Example 1 It is a block diagram of a drive gear apparatus.
  • Example 2 It is a top view of meshing
  • Example 2 It is a block diagram of a differential gear apparatus.
  • Conventional example 1) It is a perspective view of a spur gear differential.
  • (Conventional example 2) It is a block diagram of a transmission device. (Conventional example 3)
  • Example 1 A drive gear device 10 of Example 1 will be described with reference to FIGS.
  • FIG. 1 is an explanatory diagram schematically showing the configuration of the drive gear device 10 by taking an automobile drive as an example.
  • 2 to 5 are perspective views showing the meshing of the gears of the drive gear device 10.
  • the spur gear is illustrated for explanation, it is not limited to the spur gear, and an appropriate type of gear may be selected.
  • the drive gear device 10 includes first and second planetary gear mechanisms 11 a and 11 b, a coupling shaft 12, and first and second auxiliary gear members 18 and 19. ing.
  • the first and second planetary gear mechanisms 11a and 11b include (i) external-tooth sun gear members 12a and 12b on which external-tooth sun gears are formed, and (ii) ) A plurality of planetary gear members 14a, 14b formed with planetary gears meshed with the external gear sun gear, and (iii) internal teeth 16a, 17a meshed with the planetary gears, which are radially outer than the internal teeth 16a, 17a. And (iv) planetary carriers 15a and 15b that support the planetary gear members 14a and 14b so as to rotate and revolve freely. As shown in FIGS.
  • the planetary gear members 14a and 14b are rotatably supported on the support shafts 15p and 15q of the planet carriers 15a and 15b, and the center axes 15s and 15t of the planet carriers 15a and 15b are rotated. Is transmitted to the left and right wheels 2a, 2b, for example.
  • externally toothed sun gear members 12 a and 12 b of the first and second planetary gear mechanisms 11 a and 11 b are coaxially fixed to the coupling shaft 12.
  • the coupling shaft 12 is coaxially fixed with an intermediate gear member 13 formed with external teeth that mesh with the drive input gear 30 between the external sun gear members 12a and 12b.
  • the coupling shaft 12 is a coupling member.
  • the diameter of the addendum circle of the intermediate gear member 13 fixed to the coupling shaft 12 is the diameter of the addendum circles of the external teeth 16b and 17b of the internal gear members 16 and 17 of the first and second planetary gear mechanisms 11a and 11b. It is preferable to make it smaller. In this case, since the intermediate gear member 13 does not protrude, it is easy to configure so as not to interfere with the first and second auxiliary gear members 18 and 19, and the drive gear device 10 can be reduced in size. Moreover, the rotation center axis
  • a plurality of sets, for example, three sets of first and second auxiliary gear members 18 and 19 are arranged outside the internal gear members 16 and 17 of the first and second planetary gear mechanisms 11a and 11b.
  • the first and second planetary gear mechanisms 11a and 11b are arranged so as to be parallel and rotatable with the rotation center axes of the externally toothed sun gear members 12a and 12b.
  • the first auxiliary gear member 18 includes a first gear 18a that meshes with the external teeth 16b of the internal gear member 16 of the first planetary gear mechanism 11a, and a third gear 18b.
  • the gears 18a and 18b are arranged coaxially.
  • the second auxiliary gear member 19 includes a second gear 19a that meshes with the external teeth 17b of the internal gear member 17 of the second planetary gear mechanism 11b, and a fourth gear 19b.
  • the gears 19a and 19b are arranged coaxially.
  • the third gear 18b of the first auxiliary gear member 18 and the fourth gear 19b of the second auxiliary gear member 19 are engaged with each other.
  • the internal gear members 16 and 17 of the first and second planetary gear mechanisms 11a and 11b are omitted from the illustration of the internal teeth 16a and 17a.
  • the third auxiliary gear member 5 fixed to the rotating shaft 4a of the control motor 4 is disposed outside the internal gear member 17 of the second planetary gear mechanism 11b.
  • the third auxiliary gear member 5 is formed with external teeth that mesh with the external teeth 17b of the internal gear member 17 of the second planetary gear mechanism 11b.
  • the third auxiliary gear member 5 may be arranged to mesh with one of the first and second gears 18 a, 19 a of the first and second auxiliary gear members 18, 19. It is also possible to arrange so as to mesh with any one of the third and fourth gears 18b and 19b of the auxiliary gear members 18 and 19.
  • the coupling shaft 12, the central shafts 15s and 15t of the planetary carriers 15a and 15b, and the first and second auxiliary gear members 18 and 19 are rotatably supported on the casing via, for example, bearings. Then, the control motor 4 is fixed to the casing.
  • the first and second gears 18a, 19a of the first and second auxiliary gear members 18, 19 are connected to the external teeth 16b, 17b of the inner gear members 16, 17 of the first and second planetary gear mechanisms 11a, 11b.
  • the first and second auxiliary gear members 18 and 19 have first and second auxiliary gear members 18 and 19 from the external teeth 16b and 17b of the first and second planetary gear mechanisms 11a and 11b.
  • Forces Fa and Fb are transmitted to the second gears 18b and 19b.
  • the forces Fa and Fb are balanced via the auxiliary gear members 18 and 19, and the distribution of the rotational torques Ta and Tb is maintained.
  • the external teeth 16b and 17b of the internal gear members 16 and 17 of the first and second planetary gear mechanisms 11a and 11b and therefore the first and second The difference in rotational speed is transmitted from one of the auxiliary gear members 18 and 19 to the other, while the distribution of the rotational torques Ta and Tb remains unchanged, the difference between the forces Fa and Fb does not occur, and the rotational torques Ta and Tb are evenly distributed. Will come to be.
  • the drive gear device 10 includes the first and second auxiliary gear members 18 and 19 so that the drive gear device 10 has the center shafts 15s and 15t of the planet carriers 15a and 15b of the first and second planetary gear mechanisms 11a and 11b. Rotational energy can be evenly distributed.
  • the drive gear device 10 includes the third auxiliary gear member 5 in addition to the first and second auxiliary gear members 18 and 19, so that the planetary carriers of the first and second planetary gear mechanisms 11 a and 11 b are provided.
  • the distribution of rotational energy with respect to the central shafts 15s and 15t of 15a and 15b can be controlled by the third auxiliary gear member 5.
  • the drive gear device 10 equalizes the rotational torques output to the center shafts 15s and 15t of the planet carriers 15a and 15b of the first and second planetary gear mechanisms 11a and 11b, or makes a difference in rotational torque. Therefore, it can be used as a differential that distributes rotational torque to the left and right and front and rear wheels.
  • one driving input gear 30 that transmits the driving force of the engine is configured to mesh with the intermediate gear member 13.
  • the drive input gear 30 a for driving the engine and the drive input gear 30 b for driving the motor are engaged with the intermediate gear member 13.
  • Table 1 An example of the number of teeth of each gear in these cases is shown in Table 1 below.
  • the drive gear device 10 has excellent actions and effects as follows.
  • first and second auxiliary gears 18 and 19 are arranged outside the internal gear members 16 and 17 of the first and second planetary gear mechanisms 11a and 11b, a force acting corresponding to the rotational torque is generated. Get smaller. Furthermore, the first and second auxiliary gears 18 and 19 can be arranged in a plurality of groups, and each group can share the force acting corresponding to the rotational torque. Therefore, it is easy to ensure the strength of the first and second auxiliary gears 18 and 19. Further, the alignment of the gear shaft inside the drive gear device 10 does not go wrong due to the rotational torque.
  • the first and second auxiliary gears 18 and 19 are rotatably supported by a casing or the like, like the coupling shaft 12 and the center shafts 15s and 15t of the planet carriers 15a and 15b, and simply rotate. Thus, unlike the planetary gear, it does not revolve around the internal gear members 16, 17 of the first and second planetary gear mechanisms 11a, 11b.
  • the first and second auxiliary gears 18 and 19 are different in the rotational speed of the center shafts 15s and 15t of the planet carriers 15a and 15b of the first and second planetary gear mechanisms 11a and 11b, that is, the wheels 2a, Since the rotation is caused only by the difference in the rotation speed of 2b, the rotation speed itself is also small.
  • the first and second auxiliary gears 18 and 19 can be made small.
  • the rotation center axes of the first and second auxiliary gear members 18 and 19 and the third auxiliary gear member 5 are the rotation centers of the first and third planetary gear mechanisms 11a and 11b.
  • the first and second auxiliary gear members 18 and 19 are arranged around the inner gear members 16 and 17 of the first and third planetary gear mechanisms 11a and 11b because they are arranged parallel to the shaft and do not change in the axial direction. Can be arranged.
  • the rotation center axes of the first and second auxiliary gear members 18, 19 and the third auxiliary gear member 5 are the rotation centers of the first and third planetary gear mechanisms 11a, 11b. Since it is arranged in parallel with the shaft and the rotating shafts do not intersect, it can be manufactured with high performance and low cost by existing technology, and there is little friction loss of meshing.
  • the drive gear device 10 can have a symmetrical shape, it is easy to ensure straight travel when used in an automobile.
  • the rotation for transmitting the rotational torque and the rotation for controlling the distribution of the rotational torque are completely separated. Even if the control motor 4 is driven, the sum of the rotational torques output from the center axes 15s and 15t of the planet carriers 15a and 15b of the first and second planetary gear mechanisms 11a and 11b does not change. For example, the control motor 4 does not affect the rotation of the drive source. Rotational torque output to the central shafts 15s and 15t of the planet carriers 15a and 15b of the first and second planetary gear mechanisms 11a and 11b even if the rotation of the driving force generated by a driving source such as a motor or an engine is changed. The control of the difference is not affected. Therefore, the drive gear device 10 has very good controllability with respect to the distribution of rotational torque and the difference in rotational speed.
  • a drive gear device 10a of Embodiment 2 will be described with reference to FIGS.
  • the drive gear device 10a of the second embodiment is configured in substantially the same manner as the drive gear device 10 of the first embodiment.
  • the same reference numerals are used for the same components as in the first embodiment, and differences from the first embodiment will be mainly described.
  • the drive gear device 10a of the second embodiment is the same as the drive gear device 10 of the first embodiment, and the external sun gear members 12a and 12b of the first and second planetary gear mechanisms 11a and 11b.
  • the first and second auxiliary gear members 18 and 19 and the third auxiliary gear member 5 are provided.
  • the drive gear device 10a of the second embodiment is different from the drive gear device 10 of the first embodiment in the configuration between the first and second planetary gear mechanisms 11a and 11b. That is, between the first and second planetary gear mechanisms 11a and 11b, the electric motor 6 with the rotating shaft 8 projecting at both ends is disposed, and at both ends of the rotating shaft 8, the first and second planetary gear mechanisms 11a are disposed. , 11b external gear sun gear members 12a, 12b are fixed. That is, the rotation shaft 8 of the electric motor 6 is a modification of the coupling shaft 12 of the drive gear device 10 of the first embodiment. An intermediate gear member 13 is fixed to one side of the rotating shaft 8.
  • the drive input gear 30 is different from the drive gear device 10 of the first embodiment, and a drive transmission gear 31 that meshes with the drive input gear 30 is rotated by a drive source.
  • a drive transmission gear 31 that meshes with the drive input gear 30 is rotated by a drive source.
  • FIG. 8A even if one set of drive input gear 30 and drive transmission gear 31 are provided, as shown in FIG. 8B, two or more sets of drive input gears 30a and 30b and drive transmission are provided. Gears 31a and 31b may be provided. If possible in terms of dimensions, the drive transmission gear 31 may be eliminated and the role of the drive input gear 30 may be assigned as in the first embodiment, or the intermediate gear member 13 and the drive input gear 30 may be non-parallel shaft gears. Absent.
  • the drive gear device 10a receives the rotational torque output to the center shafts 15s and 15t of the planetary carriers 15a and 15b of the first and second planetary gear mechanisms 11a and 11b. It is possible to evenly distribute and control the difference in the distribution of rotational torque.
  • the drive system is integrally configured by combining the electric motor, the speed reduction device, and the differential, and the drive gear device 10a is particularly suitable for an automobile driven by a motor. It is. That is, in the planetary gear mechanism, the reduction ratio is greatest when the sun outer gear is used as an input and the planet carrier is used as an output. In general automobiles, the tire travels about 1.8 to 2 m in one rotation of the tire, and the vehicle speed is about 160 Km / h. Therefore, the output rotation required for the planetary carrier is about 1200 to 1500 rpm. For motors, 5,000 rpm to 10,000 rpm is the most efficient rotational speed.
  • the drive gear device 10a can realize a motor drive system configuration that is most rational and meets the requirements of the vehicle.
  • the drive gear devices 10 and 10a can be easily reduced in size and weight with a simple configuration.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

L'invention fournit un dispositif d'engrenage d'entraînement permettant une miniaturisation et un allègement de manière aisée à l'aide d'une structure simple. Un élément de liaison (12) lie coaxialement des éléments planétaire de denture extérieure (12a, 12b) d'un premier et d'un second mécanisme d'engrenage planétaire (11a, 11b). Des dentures extérieures (16b, 17b) sont formées sur des éléments d'engrenage interne (16, 17) du premier et du second mécanisme d'engrenage planétaire (11a, 11b). Un premier élément d'engrenage auxiliaire (18) possédant un premier et un troisième engrenage (18a, 18b), et un second élément d'engrenage auxiliaire (19) possédant un second et un quatrième engrenage (19a, 19b), sont disposés de manière à permettre leur rotation et parallèlement à un axe central de rotation des éléments planétaire de denture extérieure (12a, 12b) du premier et du second mécanisme d'engrenage planétaire (11a, 11b), de sorte que le premier engrenage (18a) s'emboîte avec la denture extérieure (16b) de l'élément d'engrenage interne (16) du premier mécanisme d'engrenage planétaire (11a), que le second engrenage (19a) s'emboîte avec la denture extérieure (17b) de l'élément d'engrenage interne (17) du second mécanisme d'engrenage planétaire (11b), et que le troisième et le quatrième engrenage (18b, 19b) s'emboîtent entre eux.
PCT/JP2013/069259 2013-07-16 2013-07-16 Dispositif d'engrenage d'entraînement WO2015008325A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
PCT/JP2013/069259 WO2015008325A1 (fr) 2013-07-16 2013-07-16 Dispositif d'engrenage d'entraînement
PCT/JP2014/068161 WO2015008661A1 (fr) 2013-07-16 2014-07-08 Dispositif d'engrenage d'entraînement
EP14826409.6A EP3023672A4 (fr) 2013-07-16 2014-07-08 Dispositif d'engrenage d'entraînement
JP2015527263A JP6122119B2 (ja) 2013-07-16 2014-07-08 駆動歯車装置
US14/905,567 US10203028B2 (en) 2013-07-16 2014-07-08 Drive gear unit
CN201480040592.8A CN105556174B (zh) 2013-07-16 2014-07-08 驱动齿轮装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/069259 WO2015008325A1 (fr) 2013-07-16 2013-07-16 Dispositif d'engrenage d'entraînement

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WO2015008325A1 true WO2015008325A1 (fr) 2015-01-22

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PCT/JP2013/069259 WO2015008325A1 (fr) 2013-07-16 2013-07-16 Dispositif d'engrenage d'entraînement
PCT/JP2014/068161 WO2015008661A1 (fr) 2013-07-16 2014-07-08 Dispositif d'engrenage d'entraînement

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EP (1) EP3023672A4 (fr)
JP (1) JP6122119B2 (fr)
CN (1) CN105556174B (fr)
WO (2) WO2015008325A1 (fr)

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JP2017110682A (ja) 2015-12-14 2017-06-22 トヨタ自動車株式会社 動力伝達装置
JP6298037B2 (ja) 2015-12-24 2018-03-20 トヨタ自動車株式会社 駆動装置の制御システム
JP6414044B2 (ja) 2015-12-25 2018-10-31 トヨタ自動車株式会社 車両の駆動力制御装置
JP6378219B2 (ja) 2016-01-22 2018-08-22 トヨタ自動車株式会社 モータ駆動ユニット
JP2017141868A (ja) 2016-02-09 2017-08-17 トヨタ自動車株式会社 トルクベクタリング装置
JP6348526B2 (ja) * 2016-02-18 2018-06-27 トヨタ自動車株式会社 動力伝達装置
JP6325586B2 (ja) * 2016-02-18 2018-05-16 トヨタ自動車株式会社 モータ駆動ユニット
JP6356715B2 (ja) 2016-02-24 2018-07-11 トヨタ自動車株式会社 トルクベクタリング装置
JP6475188B2 (ja) 2016-04-28 2019-02-27 トヨタ自動車株式会社 駆動装置
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WO2015008661A1 (fr) 2015-01-22
US10203028B2 (en) 2019-02-12
JPWO2015008661A1 (ja) 2017-03-02
JP6122119B2 (ja) 2017-04-26
EP3023672A4 (fr) 2016-12-07
CN105556174A (zh) 2016-05-04
US20160153537A1 (en) 2016-06-02
CN105556174B (zh) 2018-10-19

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